EP0087743A2 - Umlaufuntersetzungsgetriebe mit Ausgleichkupplung - Google Patents

Umlaufuntersetzungsgetriebe mit Ausgleichkupplung Download PDF

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Publication number
EP0087743A2
EP0087743A2 EP83101739A EP83101739A EP0087743A2 EP 0087743 A2 EP0087743 A2 EP 0087743A2 EP 83101739 A EP83101739 A EP 83101739A EP 83101739 A EP83101739 A EP 83101739A EP 0087743 A2 EP0087743 A2 EP 0087743A2
Authority
EP
European Patent Office
Prior art keywords
rotor
drive
speed reducer
shaft
drive shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP83101739A
Other languages
English (en)
French (fr)
Other versions
EP0087743B1 (de
EP0087743A3 (en
Inventor
Michel A. Pierrat
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT83101739T priority Critical patent/ATE27049T1/de
Publication of EP0087743A2 publication Critical patent/EP0087743A2/de
Publication of EP0087743A3 publication Critical patent/EP0087743A3/en
Application granted granted Critical
Publication of EP0087743B1 publication Critical patent/EP0087743B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/48—Special means compensating for misalignment of axes, e.g. for equalising distribution of load on the face width of the teeth

Definitions

  • This invention relates to an orbital speed reducer having an improved drive system. More particularly it relates to a drive system for eliminating radial forces on the drive mechanism and thereby increasing the life of the bearing structure and facilitating the repair or interchange of drive motors.
  • the invention is embodied in a speed reducer, suitable for precision motion control applications, of the type decribed above in which a compensation coupling is interposed between the drive shaft and an orbitally driven rotor.
  • the compensation coupling is arranged to provide rotary motion of a rotor drive element or wheel carried by the rotor while permitting deviation of the rotor from its prescribed orbital path without creating radial forces on the drive shaft.
  • an orbitally-driven rotor mounted for free rotation on a rotor drive element driven in a rotary path by a drive shaft, has a perimeter defined by an epitrochoidal curve that simultaneously engages each of a series of surrounding rollers mounted on a stationary support, the number of lobes on the rotor being equal to one less than the number of surrounding rollers.
  • Rotation of the drive shaft causes the rotor to move orbitally and to rotate with a speed reduction equal to the reciprocal of the number of lobes on the rotor.
  • a similar structure may serve as a second stage with a second orbital rotor driven by the first rotor and moved orbitally by the same eccentric. The second stage provides a further speed reduction to an output drive, provided by a rotatable output disk supporting the rollers in the second stage.
  • the rotor drive element is driven in a rotary path by a variable-length crank arm that provides only rotary thrust and does not transmit radial forces to the drive shaft.
  • This compensation coupling may take the form of a driving sleeve keyed or otherwise secured to a drive shaft that extends into and makes a sliding fit within a slot in a circular rotor drive element mounted for free rotation within a rotor that follows an orbital path.
  • the driving sleeve slidably engages two opposing internal faces of the slot in the rotor drive element at points displaced radially outwardly from the axis of the drive shaft.
  • the driving sleeve thus forms a crank mechansim, the slot in the rotor drive element being long enough to permit the desired radial movement of the rotor drive element and rotor assembly.
  • Radial movement generated by the interaction of the rotor and the surrounding rollers and transmitted along a first line parallel with the longitudinal axis of the slot result only in movement of the rotor drive element along the axis of its slot and have no effect other than a slight change in the effective length of the crank arm.
  • Radial movement forces transmitted along a line perpendicular to the longitudinal axis of the slot merely aid or oppose the torque of the drive motor and result in nothing more than a slight phase shift. Movement at intermediate angles produce a combination of these two effects.
  • the drive shaft is thus protected from high radial forces irrespective of the direction of the movements that would otherwise give rise to those forces.
  • the driving surfaces of the sleeve extension at the points of contact with the opposing surfaces of the rotor drive wheel form an arc of a circle so that radial movement perpendicular to the axis of the slot will not cause locking or binding upon slight rotary movement of the rotor drive element caused by these radial movements and so that the driving surfaces will at all times remain in firm engagement with the faces of the slot and not become a source of backlash.
  • a longitudinal slot in the end of the driving sleeve divides it into two fingers, each providing one of the driving surfaces that press against the faces of the slot in the rotor drive element eccentric with a compliant force equal to or greater than the maximum torque to be developed under full load conditions. For larger units, an adjustment screw permits precise adjustment of the distance between the drive surfaces of the fingers.
  • a compensation coupling As shown in the drawings, a compensation coupling, generally indicated at 2, includes a driving sleeve 3 secured to a drive shaft 4 by a set screw 6 that engages a flat section 8 on the shaft 4. One end portion of the driving sleeve 3 is cut away to form an extension 12 that extends into a slot 14 in a rotor drive element 16 rotatably mounted in an anti-friction bearing 18 that is, in turn, rotatably retained in an opening in an orbital rotor 22.
  • rollers 24, each supported by a shaft 26, are mounted on a supporting disk 28 and arranged equally spaced in a circle to form an operating structure somewhat similar to an internal ring gear.
  • the perimeter of the rotor 22 is formed by a series of thirteen external lobes 22a defined by an epitrochoidal curve and is at all times in engagement with the rollers 24.
  • the sleeve extension 12 drives the rotor drive element 16 about a rotary path that is offset from the axis of the shaft 4 causing the rotor 22 to move orbitally, during which movement the outer surface of the rotor remains at all times in contact with each of the rollers 24.
  • This orbital movement of the rotor causes it to revolve about its own axis at a speed equal to one-thirteenth the speed of the shaft 4 and in the opposite direction.
  • the driving sleeve 3 of the compensation coupling 2 is shown in more detail in Figures 2-4.
  • a cyclindrical portion 34 of the sleeve 2 has a threaded opening 36 that receives the screw 6.
  • the extension 12, formed integrally with the cyclindrical portion 34, extends approximately one third of the distance around the full circle of the cylindrical portion 34.
  • Two opposed drive surfaces 38 and 42 of the extension 12 form, in the plane perpendicular to the longitudinal axis of the shaft 4, arcs of a circle having a diameter equal to the width of the slot 14 ( Figure 1).
  • the arcuate drive surfaces 38 and 42 remain in firm engagement with the adjacent internal faces of the slot. With an arc of greater radius, there would be an increasing likelihood of binding, and with an arc of lesser radius there would be a loss of contact giving rise to backlash or lost motion.
  • the surfaces 38 and 42 are crowned also along a direction parallel with the longitudinal axis of the sleeve 3 as shown in Figure 2.
  • the surfaces 38 and 42 of the driving sleeve 3 engage opposing rectilinear internal faces of the slot 14. To further prevent this coupling from introducing backlash or lost motion into the speed reducer and avoid any possibility of binding, the surfaces 38 and 42 are maintained at all times in close engagement with the internal faces of the slot 14.
  • the surfaces 38 and 42 are dimensioned to maintain constant pressure against the internal faces of the slot 14 and the stiffness of the fingers 12a and 12b of the sleeve 3 are such that at full driving torque there is no significant deflection of the fingers 12a and 12b.
  • the ends 46 and 48 ( Figure 1) of the slot 14 are curved and the length of the slot is great enough to allow for the radial movement of the rotor drive wheel.
  • Figure 6 shows the same sleeve extension 12 in which an adjustment screw 50 is in threaded engagement with the finger 42 and extends across the slot 44 to abut the adjacent surface of the finger 38.
  • a radial movement of rotor 22 and the rotor drive element 16, along a line y-y in Figure 1 causes the rotor drive element to move parallel with the line y-y relative to the driving sleeve 2 so that no radial force from this source is applied to the drive shaft 4 while the compensation coupling 2 continues to apply rotary force to the rotor drive wheel 16.
  • a radial movement along the line x-x creates a rotary movement against the torque of the motor, shifting the phase of the drive but the only radial force is caused by the driving torque generated by the shaft 4 and is equal to the torque divided by the length of the crank arm.
  • the shaft 4 is driven, in this example, by a pancake motor 52 ( Figure 5) suitably secured to one end of the speed reducer as by screws 54.
  • the drive shaft is supported by two bearings in the speed reducing unit, but in this example the motor drive shaft is secured to the sleeve 2 which provides the only bearing support for the shaft 4 within the speed reducing unit. This construction is possible because of the limitation of radial forces on the drive shaft 4.
  • the disk 28 is integral with the housing of the speed reducer.
  • the rotor 22 is a two-stage rotor, the second stage of which drives an output disk 56.
  • the disk 56 is mounted for rotation relative to the disk 28 by a bearing surface 58. All of the elements of this speed reducer save the compensation coupling are described more fully in my U. S. Patent 3,998,112 and the above-referenced copending applications.
  • the arrangement shown here facilitates replacement of the motor 52 since access to only one end of the speed reducing mechanism is required.
  • Motor removal is accomplished merely by removing the motor mount screws 54.
  • This method of motor removal is particularly advantageous when the speed reducer is used as a motion control device such as the motive force and positioning device for a robot arm.
  • the robot arm, or some other heavy or complex mechanism is secured to the end of the speed reducer opposite the motor and would have to be removed to replace or repair the motor in speed reducers of the types heretofore in use.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Steroid Compounds (AREA)
  • Transmission Devices (AREA)
EP83101739A 1982-02-25 1983-02-23 Umlaufuntersetzungsgetriebe mit Ausgleichkupplung Expired EP0087743B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83101739T ATE27049T1 (de) 1982-02-25 1983-02-23 Umlaufuntersetzungsgetriebe mit ausgleichkupplung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US352122 1982-02-25
US06/352,122 US4549450A (en) 1982-02-25 1982-02-25 Orbital speed reducer with compensation coupling

Publications (3)

Publication Number Publication Date
EP0087743A2 true EP0087743A2 (de) 1983-09-07
EP0087743A3 EP0087743A3 (en) 1985-01-09
EP0087743B1 EP0087743B1 (de) 1987-05-06

Family

ID=23383881

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83101739A Expired EP0087743B1 (de) 1982-02-25 1983-02-23 Umlaufuntersetzungsgetriebe mit Ausgleichkupplung

Country Status (6)

Country Link
US (1) US4549450A (de)
EP (1) EP0087743B1 (de)
JP (1) JPS58156749A (de)
AT (1) ATE27049T1 (de)
CA (1) CA1194710A (de)
DE (1) DE3371400D1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0474897A1 (de) * 1990-09-10 1992-03-18 Sumitomo Heavy Industries Co., Ltd. Planetenübersetzungsgetriebe
US8033943B2 (en) 2005-08-18 2011-10-11 Ntn Corporation In-wheel motor driving unit
FR3050504A1 (fr) * 2016-04-25 2017-10-27 Jtekt Europe Sas Reducteur cycloidal avec rattrapage automatique de jeu et systeme de direction assistee pourvu d’un tel reducteur
CN113427283A (zh) * 2021-07-30 2021-09-24 章君巧 一种自动调节等分轴距的多轴调节器

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4914330A (en) * 1989-03-09 1990-04-03 Michel Pierrat Low speed brushless electric motor
US5211611A (en) * 1989-08-01 1993-05-18 American Power Equipment Company Planocentric drive mechanism
EP0573019B1 (de) * 1992-06-03 1996-10-23 Sumitomo Heavy Industries, Ltd. Zykloidengetriebe
US6902507B2 (en) * 2002-04-11 2005-06-07 Richard N. Ballard Roller cam assembly
RU2244181C2 (ru) * 2002-10-23 2005-01-10 Институт надежности машин Национальной Академии Наук Беларуси Планетарный редуктор с внутренним зацеплением
BRPI0702377A2 (pt) * 2007-08-02 2009-03-17 Cunha Gravio Valmor Da redutor de velocidade por corrente
CN110985611A (zh) * 2019-05-22 2020-04-10 苏州华震工业机器人减速器有限公司 精密控制用中空减速机

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1942794A (en) * 1931-02-05 1934-01-09 Melvin B Benson Corp Speed reducer
US2303365A (en) * 1939-11-14 1942-12-01 Karlsen Karl Henry Clock mechanism
US2250259A (en) * 1940-03-11 1941-07-22 Jr Bradford Foote Speed reducing gearing
US3144791A (en) * 1958-06-06 1964-08-18 Aubry H Temple Speed reducer
US3045503A (en) * 1959-05-28 1962-07-24 Square D Co Control mechanism
GB955097A (en) * 1960-05-16 1964-04-15 Braren Rudolf Planetary gear
US3429393A (en) * 1966-12-08 1969-02-25 Lorence Mfg Corp Drive mechanism
BE770716A (fr) * 1971-07-30 1971-12-01 Soudure Autogene Elect Reducteur de vitesse sans friction et a grands rapports de reduction.
US3998112A (en) * 1974-12-06 1976-12-21 Compudrive Corporation Mechanical drives
US4016780A (en) * 1975-03-03 1977-04-12 Trochoidal Gear Technology, Inc. Hypotrochoidal cluster gear drives
DE2757907A1 (de) * 1977-12-24 1979-07-05 Keiper Automobiltechnik Gmbh Gelenkbeschlag fuer sitze mit verstellbarer rueckenlehne, insbesondere kraftfahrzeugsitze
US4348918A (en) * 1979-02-21 1982-09-14 Teijin Seiki Company Limited Speed change device
DE3013304C2 (de) * 1980-04-05 1983-05-11 Keiper Automobiltechnik Gmbh & Co Kg, 5630 Remscheid Stellvorrichtung für Sitze und Fenster, insbesondere von Kraftfahrzeugen

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0474897A1 (de) * 1990-09-10 1992-03-18 Sumitomo Heavy Industries Co., Ltd. Planetenübersetzungsgetriebe
US5123884A (en) * 1990-09-10 1992-06-23 Sumitomo Heavy Industries, Ltd. Planetary speed changing device
US8033943B2 (en) 2005-08-18 2011-10-11 Ntn Corporation In-wheel motor driving unit
US8038562B2 (en) 2005-08-18 2011-10-18 Ntn Corporation Power transmission device
FR3050504A1 (fr) * 2016-04-25 2017-10-27 Jtekt Europe Sas Reducteur cycloidal avec rattrapage automatique de jeu et systeme de direction assistee pourvu d’un tel reducteur
WO2017187055A1 (fr) * 2016-04-25 2017-11-02 Jtekt Europe Réducteur cycloïdal avec rattrapage automatique de jeu et système de direction assistée pourvu d'un tel réducteur
CN109073047A (zh) * 2016-04-25 2018-12-21 捷太格特欧洲公司 带有齿隙自动调节的摆线减速器和具有这种减速器的动力转向系统
US10926792B2 (en) 2016-04-25 2021-02-23 Jtekt Europe Cycloidal reducer with backlash self-adjustment and power steering system with such a reducer
CN113427283A (zh) * 2021-07-30 2021-09-24 章君巧 一种自动调节等分轴距的多轴调节器

Also Published As

Publication number Publication date
JPH0338458B2 (de) 1991-06-10
JPS58156749A (ja) 1983-09-17
EP0087743B1 (de) 1987-05-06
US4549450A (en) 1985-10-29
DE3371400D1 (en) 1987-06-11
ATE27049T1 (de) 1987-05-15
EP0087743A3 (en) 1985-01-09
CA1194710A (en) 1985-10-08

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